US6644350B1 - Variable pressure solenoid control valve - Google Patents

Variable pressure solenoid control valve Download PDF

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Publication number
US6644350B1
US6644350B1 US09/579,546 US57954600A US6644350B1 US 6644350 B1 US6644350 B1 US 6644350B1 US 57954600 A US57954600 A US 57954600A US 6644350 B1 US6644350 B1 US 6644350B1
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Prior art keywords
valve
armature
exhaust
pressurized fluid
inlet
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Expired - Fee Related
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US09/579,546
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English (en)
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John Michael Douglass
Paul Anders Christensen
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Acutex Inc
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Acutex Inc
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Priority to US09/579,546 priority Critical patent/US6644350B1/en
Priority to BR0103176A priority patent/BR0103176A/pt
Priority to EP01112061A priority patent/EP1158231B1/fr
Priority to DE2001613588 priority patent/DE60113588T2/de
Priority to CA 2348814 priority patent/CA2348814C/fr
Assigned to ACUTEX, INC. reassignment ACUTEX, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHRISTENSEN, PAUL ANDERS, DOUGLASS, JOHN MICHAEL
Priority to US10/316,405 priority patent/US6860293B2/en
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Publication of US6644350B1 publication Critical patent/US6644350B1/en
Assigned to NATIONAL CITY BANK, AS COLLATERAL AGENT reassignment NATIONAL CITY BANK, AS COLLATERAL AGENT SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ACUTEX, INC.
Assigned to ACUTEX, INC. reassignment ACUTEX, INC. RELEASE OF SECURITY INTEREST IN PATENT COLLATERAL AT REEL 016470 FRAME 0745 Assignors: NATIONAL CITY BANK
Assigned to BEAR STEARNS CORPORATE LENDING INC., AS COLLATERAL AGENT reassignment BEAR STEARNS CORPORATE LENDING INC., AS COLLATERAL AGENT FIRST LIEN INTELLECTUAL PROPERTY SECURITY AGREEMENT Assignors: ACUTEX, INC.
Assigned to BEAR STEARNS CORPORATE LENDING INC., AS COLLATERAL AGENT reassignment BEAR STEARNS CORPORATE LENDING INC., AS COLLATERAL AGENT SECOND LIEN INTELLECTUAL PROPERTY SECURITY AGREEMENT Assignors: ACUTEX, INC.
Assigned to ACUTEX, INC., HILITE INTERNATIONAL, INC., HILITE INDUSTRIES-TEXAS, INC., HILITE INDUSTRIES AUTOMOTIVE, LP reassignment ACUTEX, INC. RELEASE OF SECURITY INTERESTS AT REEL/FRAME 019781/0191, 019781/0204, AND 019783/0524 Assignors: BEAR STEARNS CORPORATE LENDING, INC.
Assigned to JPMORGAN CHASE BANK, N.A. reassignment JPMORGAN CHASE BANK, N.A. ASSIGNMENT OF SECURITY INTEREST Assignors: BEAR STEARNS CORPORATE LENDING, INC.
Assigned to JPMORGAN CHASE BANK, N.A. reassignment JPMORGAN CHASE BANK, N.A. FIRST LIEN INTELLECTUAL PROPERTY SECURITY AGREEMENT Assignors: ACUTEX, INC., HILITE INDUSTRIES AUTOMOTIVE, LP, HILITE INTERNATIONAL, INC.
Assigned to JPMORGAN CHASE BANK, N.A. reassignment JPMORGAN CHASE BANK, N.A. SECOND LIEN INTELLECTUAL PROPERTY SECURITY AGREEMENT Assignors: ACUTEX, INC., HILITE INDUSTRIES AUTOMOTIVE, LP, HILITE INTERNATIONAL, INC.
Assigned to HILITE INDUSTRIES AUTOMOTIVE, LP, ACUTEX, INC., HYDRAULIK-RING GMBH, HILITE INTERNATIONAL INC. reassignment HILITE INDUSTRIES AUTOMOTIVE, LP RELEASE OF SECURITY INTEREST IN PATENT COLLATERAL Assignors: JPMORGAN CHASE BANK N.A.
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/0624—Lift valves
    • F16K31/0634—Lift valves with fixed seats positioned between movable valve members
    • F16K31/0637—Lift valves with fixed seats positioned between movable valve members with ball shaped valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/14—Fluid pressure control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0221—Valves for clutch control systems; Details thereof
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87217—Motor

Definitions

  • This invention relates generally to a control valve for regulating fluid pressure, and in particular to a variable pressure solenoid control valve.
  • Modern automotive transmissions typically require precise electro-hydraulic solenoid valves in order to regulate the hydraulic pressure within the various clutches and spool valves typically employed in such transmissions.
  • the types of solenoid valves commonly employed in flow control valves used in automotive transmissions include: on/off solenoid valves, pulse-width-modulated (PWM) solenoid valves, and variable pressure solenoid (VPS) control valves.
  • PWM pulse-width-modulated
  • VPS variable pressure solenoid
  • VPS control valves provide a low control pressure by bleeding-off control pressure to an exhaust downstream from a very small upstream orifice. This method suffers from a number of problems.
  • the first problem is excessive leakage.
  • the transmission fluid pump is capable of maintaining pressure even with this leakage; however, when several of these VPS control valves are used in a single transmission, the pump is no longer capable of making-up for the leakage.
  • the second problem that is present in the current 2-port bleeding-off style VPS control valves is that the valves are not capable of reducing control pressure to zero in a normally-high pressure configuration.
  • the present invention is directed to overcoming one or more of the limitations of existing variable pressure solenoid control valves.
  • the movable valve includes an inlet valve for controlling the flow of pressurized fluid into the solenoid valve, and an exhaust valve for controlling the exhaust of pressurized fluid from the solenoid valve.
  • the solenoid includes a spring biased armature for displacing the movable valve, and an electromagnetic coil for generating a variable electromagnetic field in response to the electrical input signal for moving the spring biased armature.
  • a fluid control device for an automotive transmission includes a pump for generating a pressurized fluid, a spool valve operably coupled to the pump for controllably conveying the pressurized fluid from the pump to another hydraulic device, the spool valve including a pilot port for receiving a control pressure for controlling the operation of the spool valve, and a proportional variable pressure solenoid valve for receiving the pressurized fluid and generating the control pressure for controlling the operation of the spool valve in proportion to the current level of an electrical input signal.
  • the proportional variable pressure solenoid valve includes a movable valve for controlling the pressure of the control pressure in the hydraulic system, a solenoid for controlling the movement of the movable valve, and a common housing.
  • the movable valve includes an inlet valve for controlling the flow of pressurized fluid into the solenoid valve, and an exhaust valve for controlling the exhaust of pressurized fluid from the solenoid valve.
  • the solenoid includes a spring biased armature for displacing the movable valve, and an electromagnetic coil for generating a variable electromagnetic field in response to the electrical input signal for moving the spring biased armature.
  • a method of operating a variable pressure solenoid control valve for generating a control pressure for controlling the operation of an hydraulic device using a pressurized fluid in an hydraulic system in proportion to the current level of an electrical input signal including an hydraulic section including a movable valve for controlling the pressure of the control pressure and a magnetic section including a solenoid for controlling the operation of the movable valve, that includes controllably inputting pressurized fluid into the movable valve through a first port, outputting the control pressure from the movable valve through a second port, and controllably exhausting pressurized fluid from the movable valve through a third port.
  • variable pressure solenoid control valves control the pressure of a pressurized fluid in a hydraulic system in proportion to the current level of an electrical input signal by using a 3-port movable valve that includes an inlet ball valve and an exhaust ball valve.
  • the control pressure provided by the variable pressure solenoid control valves can be reduced to zero in a normally high pressure or normally low pressure configuration.
  • the present embodiments of the invention provide variable pressure solenoid control valves having increased efficiency and improved operational performance.
  • FIG. 1 is an illustration of an embodiment of an automotive transmission including a VPS control valve for controlling the operation of a spool valve for pressurizing and depressurizing a clutch.
  • FIG. 2 is an illustration of an alternative embodiment of the VPS control valve of FIG. 1 .
  • FIG. 3 is an illustration of an alternative embodiment of the VPS control valve of FIG. 1 .
  • the reference numeral 10 refers, in general, to an automatic transmission according to an embodiment of the invention that includes a VPS control valve 12 for controlling the operation of a conventional spring biased 3-port spool valve 14 including a pilot port 14 a for pressurizing or depressurizing a conventional clutch 16 .
  • the VPS control valve includes an hydraulic section 18 for generating a variable control pressure for controlling the operation of the spool valve 14 and a magnetic section 20 for controlling the operation of the hydraulic section that are connected by a common housing 22 formed of a ferromagnetic material.
  • the hydraulic section 18 includes a body 24 defining a central through bore 26 and having an annular flange 28 that is received within an end of the housing 22 .
  • the bore 26 includes a inlet 30 for receiving a pressurized fluid from a pump 32 , an inlet seating passage 34 for receiving and supporting an inlet seating member 36 , a control exhaust passage 38 for exhausting a portion of the pressurized fluid into radially oriented control exhaust passages 40 a and 40 b , a pintle passage and orifice 42 for receiving an end of a pintle 44 and limiting the rate of fluid flow, an exhaust seat 46 for receiving an exhaust ball valve 48 and exhausting a portion of the pressurized fluid into exhaust passages 50 a and 50 b , and an opening 52 .
  • a disc filter 54 is also received within the inlet 30 of the bore 26 for filtering foreign materials out of the pressurized fluid.
  • the inlet seating member 36 defines a central through bore 56 that includes an inlet 58 at one end for receiving the pressurized fluid, and an inlet seat 60 and a pintle opening and orifice 62 at another end for receiving an inlet ball valve 64 and receiving another end of the pintle 44 and limiting the rate of fluid flow, respectively.
  • a inlet ball valve stop 66 is supported in the inlet 60 of the bore 56 for limiting the movement of the inlet ball valve 64 .
  • a pintle support member 68 slidingly supports a middle portion of the pintle 44 and is received within the control exhaust passage 38 for supporting the pintle 44 within the control exhaust passage 38 .
  • the magnetic section 20 includes a non-metallic bobbin 70 defining a central through bore 72 and including annular flanges, 74 and 76 , at opposite ends.
  • An electromagnetic coil 78 is wound around the bobbin 70 between the annular flanges 74 and 76 for generating a variable magnetic field in response to a variable current and thereby actuating an armature 80 formed of a ferromagnetic material.
  • the armature 80 is received within the bore 72 and includes a reduced diameter end member 82 , a shoulder 84 , a main body 86 , and a reduced diameter end member 88 .
  • a sleeve 90 surrounds and contains the bobbin 70 , coil 78 , and armature 80 within the housing 22 .
  • a controller 90 is operably coupled to the coil 78 for controlling the operation of the coil by supplying a variable current.
  • a flat diaphragm 92 defining a central through bore 94 for receiving the end member 82 of the armature 80 is positioned within a recessed portion 96 of the end face 98 of the annular flange 28 of the body 24 within the housing 22 .
  • a suspension washer 100 defining a central through bore 102 for receiving the end member 82 of the armature 80 is positioned proximate an end face of the flat diaphragm 92 and the shoulder 84 of the armature 80 within the housing 22 .
  • a flux washer 104 defining a central through bore 106 for receiving the main body of the armature 80 is positioned proximate the end face 98 of the annular flange 28 of the body 24 and the end face of suspension washer 100 within the housing 22 for concentrating the electromagnetic flux of the coil 78 at the front end of the armature 80 .
  • a wave washer 108 defining a central through bore 110 for receiving the main body 86 of the armature 80 is positioned proximate an end face of the flux washer 104 and the end faces of the annular flange 74 of the bobbin 56 and the sleeve 76 within the housing 22 .
  • a polepiece 112 formed of a ferromagnetic material and defining a central through bore 114 for receiving the end member 88 of the armature 80 is positioned proximate the end faces of the annular flange 76 of the bobbin 70 and the sleeve 90 within the housing 22 .
  • a resilient suspension washer 116 defining a central through bore 118 for receiving the end member 88 of the armature 80 is positioned proximate an end face of the polepiece 112 within the housing 22 .
  • a calibration hub 120 defining a central through bore 122 that includes a internally threaded portion 124 is positioned proximate to an end face of the suspension washer 116 and also connected to and positioned within an end portion of the housing 22 .
  • a spring calibration screw member 126 is positioned within the bore 122 that includes a central cavity 128 and threadedly coupled to the threaded portion 124 of the calibration hub 120 .
  • An annular armature ring 130 formed of a ferromagnetic material is connected to the end member 88 of the armature 80 proximate the end face of the main body 86 of the armature and received within the pole piece 112 .
  • the variable magnetic field generated by the coil 78 is coupled to the polepiece 112 through the housing 22 thereby actuating the armature 80 and ring armature 130 in the direction of the polepiece 112 . In this manner, the positioning of the ring armature 130 relative to the coil 78 and the polepiece 112 controls the mode of operation of the VPS control valve 12 .
  • An annular spacing ring 132 defining a central through bore 134 for receiving the end member 88 of the armature 80 is positioned between opposite end faces of the suspension washer 116 and armature ring 130 .
  • a spring 136 is positioned between the end face of the suspension washer 116 and the end face of the central cavity 128 of the screw member 126 in order to apply a biasing spring force on the armature 80 .
  • the pump 32 supplies a pressurized fluid to the inlet 30 of the body 24 of the VPS control valve 12 and the inlet of the spool valve 14 .
  • the level of control pressure exhausted from the exhaust passage 40 a of the body 24 of the VPS control valve 12 to the pilot port 14 a of the spool valve 14 is varied.
  • the spool valve 14 controllably pressurizes or depressurizes the clutch 16 .
  • the controller 90 supplies a variable current to the coil 78 in order to generate a variable magnetic field.
  • the armature 80 and armature ring 130 are displaced in the longitudinal direction from left-to-right in the direction of the polepiece 112 and against the biasing force provided by the spring 136 in the longitudinal direction from right-to-left due to the variable magnetic field generated by the coil 78 .
  • the pressurized fluid injected into the inlet 30 of the body 24 of the VPS control valve 12 applies a fluid force onto the inlet ball valve 64 in the longitudinal direction from left-to-right.
  • the applied fluid force in turn is transmitted from the inlet ball valve 64 to the pintle 44 , exhaust ball valve 48 , the end face of the end member 82 of the armature 80 and the spring 136 .
  • the applied fluid force maintains the movable members, the inlet ball valve 64 , the pintle 44 , the exhaust ball valve 48 , and the armature 80 in contact with one another and applies a substantially constant force on the armature 80 .
  • the longitudinal displacement of the armature 80 in turn displaces in turn the exhaust ball valve 48 , pintle 44 , and inlet ball valve 64 .
  • the longitudinal spacings between the inlet ball valve 64 and exhaust ball valve 48 and the inlet and outlet seats, 60 and 46 , respectively, determine the level of control pressure exhausted from the exhaust passage 40 a of the body 24 of the VPS control valve 12 to the pilot port 14 a of the spool valve 14 .
  • the amount of control pressure exhausted from the exhaust passage 40 a of the body 24 of the VPS control valve 12 to the pilot port 14 a of the spool valve 14 is decreased.
  • VPS control valve 12 is calibrated to provide the following operational characteristics:
  • the spring biasing force provided by the spring 136 is substantially equal to the fluid force applied to the inlet ball valve 64 , pintle 44 , exhaust ball valve 48 , and armature 80 , the air gap between the armature ring 130 and the polepiece 112 is a maximum, and the magnetic force is zero.
  • the spring force is a maximum and opposing the magnetic force, and the air gap between the armature ring 130 and the polepiece 112 is reduced by approximately 0.016 inches.
  • the VPS control valve 12 provides a normally high control pressure mode of operation.
  • the reference numeral 140 refers, in general, to an alternative embodiment of a VPS control valve for use in the system 10 for controlling the operation of the conventional 3-port spool valve 14 for pressurizing or depressurizing the conventional clutch 16 .
  • the design and operation of the VPS control valve 140 is substantially identical to the VPS control valve 12 except that: (1) the orientation of the polepiece 112 is reversed; (2) the orientation of the ring armature 130 is reversed; and (3) the relative positions of the ring armature 130 and annular spacing ring 132 are reversed. In this manner, the VPS control valve 140 provides a normally low control pressure mode of operation.
  • the pump 32 supplies a pressurized fluid to the inlet 30 of the body 24 of the VPS control valve 140 and the inlet of the spool valve 14 .
  • the level of control pressure exhausted from the exhaust passage 40 a of the body 24 of the VPS control valve 12 to the pilot port 14 a of the spool valve 14 is varied.
  • the spool valve 14 controllably pressurizes or depressurizes the clutch 16 .
  • the controller 90 supplies a variable current to the coil 78 in order to generate a variable magnetic field.
  • the armature 80 and armature ring 130 are displaced in the longitudinal direction from right-to-left towards the polepiece 112 due to the variable magnetic field generated by the coil 78 .
  • the pressurized fluid injected into the inlet 30 of the body 24 of the VPS control valve 140 applies a fluid force onto the inlet ball valve 64 in the direction from left-to-right.
  • the applied fluid force in turn is transmitted from the inlet ball valve 64 to the pintle 44 , exhaust ball valve 48 , the end face of the end member 82 of the armature, and the spring 136 .
  • the applied fluid force maintains the movable members, the inlet ball valve 64 , the pintle 44 , the exhaust ball valve 48 , and the armature 80 in contact with one another and a substantially constant force is applied to the armature 80 .
  • the longitudinal displacement of the armature 80 in turn displaces in turn the exhaust ball valve 48 , pintle 44 , and inlet ball valve 64 .
  • the longitudinal spacings between the inlet ball valve 64 and exhaust ball valve 48 and the inlet and outlet seats, 60 and 46 , respectively, determine the level of control pressure exhausted from the exhaust passage 40 a of the body 24 of the VPS control valve 140 to the pilot port 14 a of the spool valve 14 .
  • the amount of control pressure exhausted from the exhaust passage 40 a of the body 24 of the VPS control valve 140 to the pilot port 14 a of the spool valve 14 is decreased.
  • VPS control valve 140 is calibrated to provide the following operational characteristics:
  • the magnetic force is substantially equal to the fluid force applied to the inlet ball valve 64 , pintle 44 , exhaust ball valve 48 , and armature 80 , and the air gap between the armature ring 130 and the polepiece 112 is a minimum.
  • the spring force is a maximum and opposing the fluid force, and the air gap between the armature ring 130 and the polepiece 112 is increased by approximately 0.016 inches.
  • the control pressure is equal to zero, there is no leakage of fluid from the VPS control valve 140 .
  • the VPS control valve 140 provides a normally low control pressure mode of operation.
  • the reference numeral 142 refers, in general, to an alternative embodiment of a VPS control valve for use in the transmission 10 for controlling the operation of the conventional 3-port spool valve 14 for pressurizing or depressurizing the conventional clutch 16 .
  • the design and operation of the VPS control valve 142 is substantially identical to the VPS control valve 12 except that the hydraulic section 18 is replaced with an hydraulic section 144 that includes a body 146 defining a central through bore 148 and having an annular flange 150 including a recess 152 for receiving the flat diaphragm 92 that is received within an end of the housing 22 .
  • the bore 148 includes a inlet 154 for receiving a pressurized fluid from the pump 32 , an inlet chamber 156 , an orifice 158 , an exhaust seat 160 for receiving an exhaust ball valve 162 and exhausting a portion of the pressurized fluid into exhaust passages 164 a and 164 b , and an opening 166 for receiving the end member 102 of the armature 80 .
  • a disc filter 168 is also received within the inlet 154 of the bore 148 for filtering foreign materials out of the pressurized fluid.
  • the pump 32 supplies a control pressure to the inlet 154 of the body 146 of the VPS control valve, 142 and the pilot port 14 a of the spool valve 14 .
  • the level of control pressure provided to the pilot port 14 a of the spool valve 14 is varied by controllably bleeding off the control pressure.
  • a pressurized supply of fluid is provided to the inlet of the spool valve 14 . In this manner, the spool valve 14 controllably pressurizes or depressurizes the clutch 16 .
  • the controller 90 supplies a variable current to the coil 78 in order to generate a variable magnetic field.
  • the armature 80 and armature ring 130 are displaced in the longitudinal direction from right-to-left towards the polepiece 112 due to the variable magnetic field generated by the coil 78 .
  • the pressurized fluid injected into the inlet 154 of the body 146 of the VPS control valve 142 applies a fluid force onto the exhaust ball valve 162 in the longitudinal direction from left-to-right.
  • the applied fluid force in turn is transmitted from the exhaust ball valve 162 to the end face of the end member 82 of the armature 80 , and the spring 136 .
  • the applied fluid force maintains the movable members, the exhaust ball valve 162 and the armature 80 in contact with one another and a substantially constant force is applied to the armature 80 .
  • the longitudinal displacement of the armature 80 in turn displaces the exhaust ball valve 162 .
  • the longitudinal spacing between the exhaust ball valve 162 and the outlet seat 160 determines the level of control pressure exhausted from the exhaust passage 164 a of the body 146 of the VPS control valve 142 to a fluid reservoir.
  • the pump 32 supplies a pressurized fluid to the inlet 154 of the body 146 of the VPS control valve 142 and the inlet of the spool valve 14 .
  • a variable control pressure is exhausted to the pilot port 14 a of the spool valve 14 from the exhaust passage 164 a of the body 146 of the VPS control valve 142 .
  • the spool valve 14 controllably pressurizes or depressurizes the clutch 16 .
  • the wave washer 108 and sleeve 90 support the pole-piece 112 while the calibration hub 120 is positioned into place within the housing 22 thereby setting the magnetic air-gap between the ring armature 130 and the pole-piece 112 . In this manner, all component tolerances are nullified and adjusted out of the completed VPS control valves 18 and 140 . Once the maximum air-gap has been set, the housing 22 is crimped-inward from the sides fixing the position of the flux-washer 104 , the pole-piece 112 and the calibration hub 120 relative to the housing 22 .
  • the adjustment of the position of the inlet seating member 36 within the inlet seating passage 34 of the body 24 all component tolerances are nullified and adjusted out of the assembly.
  • the inlet seating member 36 is pushed into the body 24 , thereby displacing the pintle 44 and pintle support 68 , until the exhaust ball valve 48 is pushed away from the exhaust seat 46 the desired distance. In this manner, the travel of the ball valves 64 and 48 are determined in the VPS control valves 18 and 140 .
  • variable pressure solenoid control valves can control the pressure of a pressurized fluid in a hydraulic system in proportion to the current level of an electrical input signal by using a 3-port movable valve that includes an inlet ball valve and an exhaust ball valve.
  • the control pressure provided by the variable pressure solenoid control valves can be reduced to zero in a normally high pressure or normally low pressure configuration.
  • the present embodiments of the invention provide variable pressure solenoid control valves having increased efficiency and improved operational performance.
  • VPS valves of the present disclosure can be incorporated into a valve module in an automatic transmission by replacing the body 24 or 146 with a cast or molded body that is common to all of the valves in the valve module.
  • the exhaust ball valves 48 and 162 may be omitted, and the end member 82 of the armature 80 modified to be received within the exhaust seat 46 to thereby directly control the exhaust of pressurized fluids from the VPS control valves 12 , 140 and 142 .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Magnetically Actuated Valves (AREA)
US09/579,546 2000-05-26 2000-05-26 Variable pressure solenoid control valve Expired - Fee Related US6644350B1 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US09/579,546 US6644350B1 (en) 2000-05-26 2000-05-26 Variable pressure solenoid control valve
BR0103176A BR0103176A (pt) 2000-05-26 2001-05-24 Válvula de controle solenóide de pressão variável
EP01112061A EP1158231B1 (fr) 2000-05-26 2001-05-25 Soupape de commande à solénoide pour des pressions variables
DE2001613588 DE60113588T2 (de) 2000-05-26 2001-05-25 Magnetisches Steuerventil für variable Drücke
CA 2348814 CA2348814C (fr) 2000-05-26 2001-05-25 Electrorobinet a pression variable
US10/316,405 US6860293B2 (en) 2000-05-26 2002-12-10 Variable pressure solenoid control valve

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Application Number Priority Date Filing Date Title
US09/579,546 US6644350B1 (en) 2000-05-26 2000-05-26 Variable pressure solenoid control valve

Related Child Applications (1)

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US10/316,405 Continuation US6860293B2 (en) 2000-05-26 2002-12-10 Variable pressure solenoid control valve

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US6644350B1 true US6644350B1 (en) 2003-11-11

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US09/579,546 Expired - Fee Related US6644350B1 (en) 2000-05-26 2000-05-26 Variable pressure solenoid control valve
US10/316,405 Expired - Fee Related US6860293B2 (en) 2000-05-26 2002-12-10 Variable pressure solenoid control valve

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US10/316,405 Expired - Fee Related US6860293B2 (en) 2000-05-26 2002-12-10 Variable pressure solenoid control valve

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US (2) US6644350B1 (fr)
EP (1) EP1158231B1 (fr)
BR (1) BR0103176A (fr)
CA (1) CA2348814C (fr)
DE (1) DE60113588T2 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040045611A1 (en) * 2002-09-06 2004-03-11 Avila Miguel I. Low leak pressure control actuator
US20040261863A1 (en) * 2003-06-25 2004-12-30 Weber Alexis C. 3/2 Normally closed module
US20050279415A1 (en) * 2004-06-14 2005-12-22 Minebea Company, Ltd. Servo valve with miniature embedded force motor with stiffened armature
US20060181144A1 (en) * 2005-02-16 2006-08-17 Bendix Commercial Vehicle Systems, Llc Solenoid armature with integrated spherical soft seal
US20070209723A1 (en) * 2006-03-07 2007-09-13 Santos Burrola Actuating valve with ball column actuation
US20070246111A1 (en) * 2006-04-19 2007-10-25 Santos Burrola Actuating valve with control port vent to ameliorate supply pressure fluctuation
US20070246015A1 (en) * 2006-04-19 2007-10-25 Alejandro Moreno Solenoid-operated valve with coil for sensing plunger position
US20080178949A1 (en) * 2007-01-31 2008-07-31 Alejandro Moreno Actuating valve with dual balls connected by pin
US9429175B2 (en) 2010-05-11 2016-08-30 Parker-Hannifin Corporation Pressure compensated hydraulic system having differential pressure control
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US7121189B2 (en) * 2004-09-29 2006-10-17 Caterpillar Inc. Electronically and hydraulically-actuated drain value
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JP6317975B2 (ja) * 2014-03-28 2018-04-25 浜名湖電装株式会社 ソレノイド装置
CN104390031B (zh) * 2014-11-04 2017-07-21 浙江大学 高压大推力两位三通球阀结构
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US11009144B2 (en) * 2019-01-03 2021-05-18 RB Distribution, Inc. Solenoid control valve
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CN111306125B (zh) * 2020-02-29 2021-08-17 杭州师范大学钱江学院 一种定点限位式多稳态换向阀及其工作位切换方法

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Cited By (17)

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Publication number Priority date Publication date Assignee Title
US6866063B2 (en) * 2002-09-06 2005-03-15 Delphi Technologies, Inc. Low leak pressure control actuator
US20040045611A1 (en) * 2002-09-06 2004-03-11 Avila Miguel I. Low leak pressure control actuator
US20040261863A1 (en) * 2003-06-25 2004-12-30 Weber Alexis C. 3/2 Normally closed module
US6874533B2 (en) * 2003-06-25 2005-04-05 Delphi Technologies, Inc. 3/2 Normally closed module
US20050279415A1 (en) * 2004-06-14 2005-12-22 Minebea Company, Ltd. Servo valve with miniature embedded force motor with stiffened armature
US7455075B2 (en) * 2004-06-14 2008-11-25 Minebea Co., Ltd. Servo valve with miniature embedded force motor with stiffened armature
US7367636B2 (en) 2005-02-16 2008-05-06 Bendix Commercial Vehicle Systems, Llc Solenoid armature with integrated spherical soft seal
US20060181144A1 (en) * 2005-02-16 2006-08-17 Bendix Commercial Vehicle Systems, Llc Solenoid armature with integrated spherical soft seal
US20070209723A1 (en) * 2006-03-07 2007-09-13 Santos Burrola Actuating valve with ball column actuation
US20070246015A1 (en) * 2006-04-19 2007-10-25 Alejandro Moreno Solenoid-operated valve with coil for sensing plunger position
US20070246111A1 (en) * 2006-04-19 2007-10-25 Santos Burrola Actuating valve with control port vent to ameliorate supply pressure fluctuation
US20080178949A1 (en) * 2007-01-31 2008-07-31 Alejandro Moreno Actuating valve with dual balls connected by pin
US9429175B2 (en) 2010-05-11 2016-08-30 Parker-Hannifin Corporation Pressure compensated hydraulic system having differential pressure control
US20180010519A1 (en) * 2016-07-06 2018-01-11 United Technologies Corporation Nacelle anti ice system
US10450955B2 (en) * 2016-07-06 2019-10-22 United Technologies Corporation Nacelle anti ice system
US11060454B2 (en) * 2016-07-06 2021-07-13 Raytheon Technologies Corporation Method of regulating air pressure in anti-icing system
US11105433B2 (en) * 2019-10-16 2021-08-31 Sun Hydraulics, Llc Pressure reducing-relieving valve

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US20030084946A1 (en) 2003-05-08
DE60113588T2 (de) 2006-06-22
US6860293B2 (en) 2005-03-01
EP1158231B1 (fr) 2005-09-28
EP1158231A3 (fr) 2003-03-26
CA2348814A1 (fr) 2001-11-26
EP1158231A2 (fr) 2001-11-28
BR0103176A (pt) 2002-07-23
DE60113588D1 (de) 2006-02-09

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